DE102007004187A1 - Adjustable coolant pump - Google Patents

Abstract

The invention has for its object to develop a continuously variable coolant pump for motor vehicles, which is driven neither by a pulley from the crankshaft of the engine nor by an electric motor and allows an increased cooling capacity almost "without" power limitation and thereby has a high overall efficiency , also requires a minimum of space with minimal weight and at the same time simple and inexpensive to produce and also works reliably even under very high ambient temperatures and susceptible to interference. The controllable coolant pump according to the invention with a pump housing (1), an impeller (3) arranged on the pump shaft (2) in the pump housing (1) is characterized, inter alia, by the end of the pump shaft (2) opposite the impeller (3) protrudes into an oil motor (4) and that in the oil motor (4) a pair of gears is arranged such that one of the two gears (7) on the pump shaft (2) is arranged rotationally fixed and the other gear (7) on a rotationally fixed in the oil motor housing (5) arranged axis (9) is mounted rotatably and displaceably, wherein in the oil motor housing (5) at least one with an inlet orifice (28) provided sleeve (29) is arranged, which with one end, opposite from the supply kidney connected to the oil inlet , in the connected to the oil inlet wheel chamber (27) opens and there flush with this wheel chamber ...

Description

The The invention relates to a controllable coolant pump for Internal combustion engines.

A direct coupling of the impeller of a coolant pump with the crankshaft of the internal combustion engine, for example one Motor vehicle has the consequence that the subsidized each Coolant volume flow determined by the speed of the motor becomes.

Therefore is always the most extreme case of need for the design of the coolant pump, d. H. the coolant pump is designed so that even at low speed and high engine load - for example when driving uphill with trailer - a sufficient Cooling performance is achieved. This circumstance causes that these non-controllable coolant pumps in the average Driving in a very low-efficiency operating point work.

Around the disadvantages of this directly driven by the crankshaft coolant pump to be eliminated in the prior art via a pulley driven by the crankshaft, controllable coolant pumps for internal combustion engines described above.

As a general rule is characteristic of these designs that the maximum achievable speed of the impeller of the maximum speed corresponds to the pump shaft driven by the crankshaft.

These transmitted from the crankshaft via a pulley on the pump shaft maximum speed of the impeller can now be at the different prescribed in the prior art, adjustable, from the crankshaft driven coolant pumps, with the most diverse technical Funds are reduced.

For example, describe the JP 62-210287 A1 , the DE 42 03 381 A1 as well as the DE 197 01 993 A1 different types of controllable, driven by a pulley coolant pumps. In these vg. Solutions provide different types of switchable magnetic couplings depending on the operating temperature of the coolant a connection between the impeller and the pulley forth.

In another, in the DE 197 52 372 A1 featured design of a controllable also driven by the crankshaft coolant pump, the impeller in the warm-up phase is arranged to rotate freely on the pump shaft driven by the crankshaft.

First when the operating temperature reaches the impeller by the contact pressure of a thermocouple from the pump shaft taken.

With all of the aforementioned, previously described in the prior art designs adjustable pulley driven coolant pumps Can the particular large-volume engines occurring hot idling problems are not solved become.

The applicant was therefore in the EP 1 275 850 B1 a proven in the meantime, also driven by a pulley coolant pump presented. In this last-mentioned solution, the impeller speed initially determined by the pulley speed can be increased as required by means of an electric motor, so that a multiplicity of the disadvantages of the pulley-driven designs of coolant pumps could be avoided by this temporarily proven solution.

However, in the prior art are also, such as, inter alia, in the patent applications DE 100 12 662 A1 ; DE 100 12 663 A1 and DE 103 14 526 A1 disclosed by the applicant, controllable coolant pumps which are driven exclusively by electric motors.

disadvantage this driven by electric motors coolant pumps exist for example in the very high construction volume (required space) as well as in the very high weight. In addition, these have electric motor driven coolant pumps a very unfavorable Overall efficiency which results from the interaction of combustion engine, Alternator, battery, electric motor and pump results since the individual not exactly optimal efficiencies of these assemblies overlap in cooperation.

One Another disadvantage of this exclusively by electric motors driven coolant pumps results from the mostly to 12 V limit on-board network of many motor vehicles which the maximum recording power of usable electric motor limited to about 330 W.

there is the control electronics of the electric motor driven coolant pumps, due to the high temperatures prevailing in the engine area, also still very susceptible to trouble.

In the prior art, however, coolant pumps are also known which are driven instead of a pulley or an electric motor by a separate, coupled in place of a pulley on the water pump hydraulic motor become. In this case, controlled bypass lines are arranged in the oil circuit of these hydraulic motors by means of separate pilot valves.

These On the one hand, solutions require very high production costs and the Monday and again need a very high construction volume with high dead weight of the unit. In addition, kick inevitably due to the different valve arrangements Pressure losses on which also an unfavorable overall efficiency have as a consequence

Of the Invention is therefore the object of a continuously variable Develop coolant pump for motor vehicles which avoids the aforementioned disadvantages, neither one Pulley from the crankshaft of the engine still from an electric motor is driven, thereby increasing cooling capacity almost "without" performance limitation possible and at the same time a high overall efficiency has, but only a minimal amount of space at minimized Takes weight and at the same time easy and inexpensive can be produced and even under very high ambient temperatures reliable and trouble-free works.

According to the invention this task by a continuously variable coolant pump for motor vehicles with the features of the main claim of Invention solved.

advantageous Designs, details as well as other features of Invention will become apparent from the dependent claims and the subsequent description of the invention Embodiment in conjunction with the drawings to the solution according to the invention.

following Now, the invention with reference to an embodiment explained in more detail in conjunction with five figures become.

It show:

1 the continuously variable coolant pump according to the invention for internal combustion engines in the side view in section (in accordance with AA 3 );

2 the continuously variable coolant pump according to the invention for internal combustion engines according to 1 , in section along the center axis of the pump shaft 2 ;

3 the continuously variable coolant pump according to the invention for internal combustion engines according to 1 in one between the gear pair and the pressure relief holes 13 lying section through the oil engine;

4 the continuously variable coolant pump according to the invention for internal combustion engines according to 1 in a section laid by the gear pair of the oil motor;

5 the detail of the oil engine 1 , with the axis 9 , the gear 7 , the working piston 16 and the reciprocating piston 23 in the working position of the reciprocating piston "fully open".

The 1 shows the inventive, continuously variable coolant pump for internal combustion engines with a pump housing 1 , one in the pump housing 1 non-rotatably on a pump shaft 2 arranged impeller 3 in the side view in section.

Essential to the invention is that the impeller 3 opposite end of the pump shaft 2 in an oil engine 4 protrudes.

It is characteristic that the oil engine 4 from an oil engine housing 5 and a front side on the oil engine housing 5 arranged lid 6 consists.

According to the invention is in the oil engine 4 a pair of gears arranged such that one of the two gears 7 on the pump shaft 2 is arranged rotationally fixed, and that the other gear 7 on a non-rotatable in the oil engine housing 5 arranged axis 9 is mounted rotatably and displaceably.

It is also characteristic that the pump shaft 2 on both sides of the gear 7 on the one hand in the oil engine housing 5 and on the other hand in the lid 6 in camps 8th is rotatably mounted.

It is advantageous if these bearings 8th are designed as plain bearings. It is also essential to the invention that in the area of the oil motor 4 both in the pump shaft 2 as well as centered in the axis, open blind holes on the lid side 10 are arranged for pressure relief, wherein in the region of the inner end of the blind holes 10 each radial bores 11 which are arranged in annular grooves 12 they open into each other in the oil engine housing 5 via pressure relief holes 13 connected to each other, wherein one of these pressure relief holes 13 via an exit opening 14 from the oil engine housing 5 features.

Essential to the invention is in this context further that in the lid 6 , centric to the axis 9 , a cylindrical piston working space 15 located in the one in its outer diameter slightly opposite to the outer diameter of the on-axis 9 arranged gear 7 larger working piston 16 is slidably mounted, wherein in the piston working space 15 between the lid 6 and the working piston 16 a compression spring 17 is arranged at engine standstill the end wall 18 of the working piston 15 in the outer edge region against this adjacent end face 19 of the oil engine housing 5 presses while on the axis 9 rotatably arranged gear 7 full of that on the pump shaft 2 arranged gear 7 engages the oil motor.

Another essential feature of the invention is that centric to the pump shaft 2 in the lid 6 a pressure relief room 20 is arranged in the front side in the pump shaft 2 arranged blind hole 10 empties.

Characteristic in this context is that in the lid front 21 a valve seat 22 is arranged such that this valve seat 21 both the piston workspace 15 as well as the pressure relief room 20 intersects, taking in this valve seat 22 sealing a valve piston 23 is arranged by means of an outside on the lid front side 21 arranged lifting magnet 24 translatory in the valve seat 22 can be moved.

The 2 shows the illustrated features of the invention, infinitely variable coolant pump for internal combustion engines, but now in a sectional view from below, along the in 1 shown center axis of the pump shaft 2 ,

It is advantageous if, as in this 2 shown, in the transition region of the oil engine housing 5 to the pump housing 1 between the pump shaft 2 and the oil engine housing 5 and / or the pump housing 1 one or more shaft seals 30 are arranged. These shaft seals are used for optimal sealing between the pump housing 1 and the oil engine housing 5 ,

In the 3 is now the infinitely variable coolant pump according to the invention for internal combustion engines in a (nach 1 ) between the gear pair and the pressure relief holes 13 lying section represented by the oil engine. At the oil engine housing 5 are an oil feed 25 and an oil drain 26 arranged each of which opens into a separate supply kidney.

A feature of the solution according to the invention consists in that with the oil feed 25 Connected supply kidney is arranged so that these partially below the Fußkreises of the on-axis 9 arranged gear 7 lies.

The 4 now shows the continuously variable coolant pump according to the invention for internal combustion engines in a (nach 1 ) cut through the gear pair of the oil motor cut.

From this illustration, another feature of the inventive solution is apparent which is that in the oil engine housing 5 at least one with an inlet panel 28 provided sleeve 29 which is arranged with one end, in which with the oil feed 25 connected wheel chamber 27 opens and there flush with this wheel chamber 27 concludes.

On the jacket of the sleeve 29 is torsion-proof of the working piston 16 slidably arranged such that the opposite end of the inlet aperture 28 provided sleeve 29 even with completely compressed compression spring 17 in the behind the working piston 16 remaining spring chamber of the piston working space 15 protrudes.

The in the 1 shown position of the reciprocating piston 23 in the valve seat 22 (Working position closed) causes now in cooperation of all features of the invention that from the oil inlet via the connected to the oil inlet wheel chamber 27 and the with the inlet panel 28 provided sleeve 29 For example, oil with a working pressure of 4 bar in the piston working space 15 flows, and thereby with the cooperation of the compression spring 17 the working piston 16 and at the same time that on the axis 9 arranged Rahnrad 7 until this completely moves with that on the pump shaft 2 arranged gear is engaged, ie on the rear wall 31 is applied.

This flows between the gear and the rear wall 31 oil in between the teeth and over the axis 9 arranged blind hole 10 , the radial bores 11 , the ring grooves 12 , the pressure relief holes 13 and the exit opening 14 For example, in the crankcase.

In this, in the 1 shown working position of the reciprocating piston 23 is from the oil engine 4 the maximum drive torque on the impeller 3 transfer.

The illustrated inventive, neither via a pulley from the crankshaft of the engine still driven by an electric motor controllable coolant pump is characterized as a result of the drive according to the invention by an increased cooling capacity (almost "without" power limitation), as at the same time by a high overall efficiency with minimal space and minimized weight 5 is now the detail of the oil engine off 1 , with the axis 9 , the gear 7 , the working piston 16 and the reciprocating piston 23 in the working position of the reciprocating piston "fully open" shown.

In this working position of the reciprocating piston 23 , by means of the impeller 3 adjacent drive torque can be reduced to a minimum, ie in this working position of the reciprocating piston 23 the impeller can be brought to a standstill, now flows, for example, under a pressure of 4 bar standing oil from the piston working space 15 over the open valve seat 22 in the pressurized example, with a pressure of 1 bar pressure relief space 20 and from there over in the pump shaft 2 arranged blind hole 10 , the radial bores 11 , the ring grooves 12 into the pressure relief hole 13 , and from there via the outlet 14 For example, in the crankcase.

According to the invention, the "openings", ie the ratio of the cross section of the inlet aperture 28 to the flow cross section at completely through the reciprocating piston 23 opened valve seat 22 so dimensioned that with completely open valve seat 22 More and more oil drains away as it can flow.

This will be the working piston 16 relieved of pressure and due to the arrangement of the oil inlet 25 connected supply kidney, which according to the invention is arranged so that these partially even below the root circle of the on-axis 9 arranged gear 7 is now on the axis 9 arranged gear 7 against the working piston 16 pressed while the working piston 16 against the action of the compression spring 16 method.

In this position of the on-axis 9 arranged gear 7 Now the oil can be taken directly from the oil feed 25 connected supply kidneys into the with the oil drain 26 Connected supply kidney flow, ie pass unhindered on the "oil engine" without pressure losses.

Will now be using the solenoid 24 the reciprocating piston 23 from the two aforementioned end positions in the valve seat 22 moved into an "intermediate position" so shifts the working piston 16 that on the axis 9 arranged gear 7 towards the back wall 31 , As a result, not all of the oil supply 25 Connected supply kidney inflowing oil "on the short way" directly into the oil drain 26 Connected supply kidney and therefore must inevitably take the "long way" on the now circumferential chambers between the teeth, ie it drives (corresponding to the position of the reciprocating piston) the gear pair with a more or less high speed.

Consequently it is by means of the solution according to the invention possible a continuously variable impeller speed the coolant pump according to the invention to realize, the present solution is simple and inexpensive can be produced and even under very high ambient temperatures very reliable and trouble-free working.

1

pump housing

2

pump shaft

3

impeller

4

motor oil

5

Oil motor housing

6

cover

7

gear

8th

camp

9

axis

10

Blind hole

11

radial bore

12

ring grooves

13

Pressure relief hole

14

outlet opening

15

Piston working space

16

working piston

17

compression spring

18

bulkhead

19

front

20

Pressure relief chamber

21

Cover front side

22

valve seat

23

reciprocating

24

solenoid

25

oil supply

26

oil drain

27

wheel well

28

inlet aperture

29

shell

30

Shaft seal

31

rear wall

QUOTES INCLUDE IN THE DESCRIPTION

This list The documents listed by the applicant have been automated generated and is solely for better information recorded by the reader. The list is not part of the German Patent or utility model application. The DPMA takes over no liability for any errors or omissions.

Cited patent literature

• - JP 62-210287 A1 [0007]
• - DE 4203381 A1 [0007]
• - DE 19701993 A1 [0007]
• DE 19752372 A1 [0008]
• - EP 1275850 B1 [0011]
• DE 10012662 A1 [0012]
• - DE 10012663 A1 [0012]
• - DE 10314526 A1 [0012]

Claims (3)

Controllable coolant pump with a pump housing ( 1 ), one in the pump housing ( 1 ) at the end against rotation on a pump shaft ( 2 ) arranged impeller ( 3 ), characterized in that - the impeller ( 3 ) opposite end of the pump shaft ( 2 ) in an oil engine ( 4 ), and - that the oil engine ( 4 ) from an oil engine housing ( 5 ) and a front side on the oil engine housing ( 5 ) arranged lid ( 6 ), and - that in the oil engine ( 4 ) a gear pair is arranged such that one of the two gears ( 7 ) on the pump shaft ( 2 ) is arranged rotationally fixed, wherein the pump shaft ( 2 ) on both sides of the Zahhnrades ( 7 ) on the one hand in the oil engine housing ( 5 ) and on the other hand in the lid ( 6 ) in warehouses ( 8th ) is rotatably mounted, and - that the other Zahrad ( 7 ) on a rotationally fixed in the oil engine housing ( 5 ) arranged axis ( 9 ) is mounted rotatably and displaceably, and - that in the region of the oil motor ( 4 ) both in the pump shaft ( 2 ) as well as centrically in the axis, blind holes open on the lid side ( 10 ) are arranged for pressure relief, wherein in the region of the inner end of the blind holes ( 10 ) Radial bores ( 11 ) are arranged which in annular grooves ( 12 ) open into each other in the oil engine housing ( 5 ) via pressure relief wells ( 13 ) and that one of the pressure relief holes via an outlet opening ( 14 ) from the oil engine housing ( 5 ), and - that is centric to the axis ( 9 ) in the lid ( 6 ) a cylindrical piston working space ( 15 ) in which a in its outer diameter slightly opposite to the outer diameter of the on the axis ( 9 ) arranged gear ( 7 ) larger working piston ( 16 ) is slidably mounted, wherein in the piston working space ( 15 ) between the lid ( 6 ) and the working piston ( 16 ) a compression spring ( 17 ) is arranged at engine standstill the end wall ( 18 ) of the working piston ( 15 ) in the outer edge region against the adjacent end face ( 19 ) of the oil engine housing ( 5 ) presses while the rotatably mounted on the axis gear ( 7 ) fully with the arranged on the pump shaft gear ( 7 ) of the oil motor; and - that centric to the pump shaft ( 2 ) in the lid ( 6 ) a pressure relief space ( 20 ) is arranged in the arranged in the pump shaft blind hole ( 10 ), and - that in the lid front side ( 21 ) a valve seat ( 22 ) is arranged such that this valve seat ( 21 ) both the piston working space ( 15 ) as well as the pressure relief space ( 20 ) and in this valve seat ( 22 ) sealing a valve piston ( 23 ) is arranged by means of an outside on the lid front side ( 21 ) arranged lifting magnet ( 24 ) translationally in the valve seat ( 22 ) can be moved, and - that on the oil engine housing ( 5 ) an oil feed ( 25 ) and an oil drain ( 26 each of which opens in each case a separate supply kidney, and - that in the oil engine housing ( 5 ) at least one with a feed orifice ( 28 ) provided sleeve ( 29 ) which is arranged with one end, into which with the oil feed ( 25 ) connected wheel chamber ( 27 ) and there flush with this wheel chamber ( 27 ), wherein at the mantle of the working piston ( 16 ) is arranged so that it can not rotate in such a way that the opposite end of the latter is provided with an inlet aperture ( 28 ) provided sleeve ( 29 ) even with completely compressed compression spring ( 17 ) in the behind the working piston ( 16 ) remaining spring chamber of the piston working space ( 15 ) protrudes. Controllable coolant pump, according to claim 1, characterized in that the bearings ( 8th ) are designed as plain bearings. Controllable coolant pump, according to claim 1, characterized in that in the transition region of the oil engine housing ( 5 ) to the pump housing ( 1 ) between the pump shaft ( 2 ) and the oil engine housing ( 5 ) and / or the pump housing ( 1 ) one or more shaft seals ( 30 ) are arranged.